JP5030381B2 - Pressure pulse generator and pressure pulse generation method - Google Patents

Abstract

A device for the generation of pressure pulses, includes a cylinder ( 3 ), a piston that is displaceably arranged in the cylinder ( 3 ), a pressure fluid circuit with an inlet ( 6 ) into and an outlet ( 7 ) out of the cylinder ( 3 ) on one side of the piston ( 4 ), a shaft ( 18 ) connected to the piston ( 4 ), and a liquid-filled chamber ( 17 ). The shaft ( 18 ) is arranged to be displaced through said chamber ( 17 ) in connection to a displacement of the piston ( 4 ) in the cylinder ( 3 ). The device includes at least one valve member ( 22, 24, 29, 32 ) for an occasional interruption of a flow of liquid out of the chamber ( 17 ).

Description

  The present patent application relates to a pressure pulse generation method and a pressure pulse generation apparatus. More particularly, this patent application relates to a method of the kind described in the preamble of claim 1 which is an independent claim and an apparatus of the kind described in the preamble of claim 14 which is an independent claim.

  The present invention is applicable to all technical fields that require generation of pressure pulses. In particular, the present invention is an application that needs to generate pressure pulses at high speed, and applies or brakes the movement of a component that is moved by the pressure pulses generated at high speed. It can be suitably used for applications that require locking a part at a desired position.

  As a technical field corresponding to this, for example, there is a technical field of an internal combustion engine. With respect to an internal combustion engine, as a method for operating and controlling an intake valve, an exhaust valve, or a fuel injection valve, a method of using a camshaft to transmit the movement of an engine piston to these valves has been conventionally employed. However, instead of this conventional method, a method of operating and controlling these valves using pressure pulses can be adopted. The present invention can also be used to operate and control a piston that is equipped to make the compression ratio of a cylinder of an internal combustion engine variable.

  Therefore, in the following description, the description will proceed in accordance with the case where the present invention is applied for the purpose of operating and controlling the intake valve or the exhaust valve of the combustion chamber of the internal combustion engine. Such an application shows one specific example of many applications of the present invention, and the application of the present invention is not limited to such an application.

  In order to drive an intake valve, an exhaust valve, or a fuel injection valve provided in a cylinder of an internal combustion engine by a pressure pulse, an actuator piston movably disposed in a cylinder-shaped pressure chamber provided corresponding to the valve The valve is connected to the actuator piston, and a pulse of a pressure fluid such as pressurized air is applied to the actuator piston to generate movement of the valve.

  The pressure fluid pulse exerts a force in a direction against the urging force of the valve spring, and the pressure fluid pulse causes the valve to move from a basic position seated on the valve seat to a remote position away from the valve seat. Will be allowed to. In order to make the valve timing variable, the valve moved to the remote position must be locked at the remote position without immediately returning to the basic position. On the other hand, it is necessary to lock the valve in the basic position, but this can be realized by the action of the valve spring.

  It is also desirable to be able to brake the movement of the valve back to the basic position so that it does not hit the valve seat violently when the valve returns to the basic position.

A first object of the present invention, for example, the intake valve equipped in the cylinder of an internal combustion engine, such as exhaust valves it fuel injection valve, a component which is adapted be moved by the pressure fluid pulses, using a hydraulic circuit Thus, it is an object of the present invention to provide a method and apparatus that enables effective locking, preferably at a given position, such as a remote position.

  The second object of the present invention is to be moved by a spring element such as a spring that is moved by a pressure fluid pulse, such as the valve described above, or a force in a direction opposite to the force from the pressure fluid pulse. It is an object of the present invention to provide a method and apparatus for enabling a part to be effectively locked before the part reaches an end position, such as a base position.

  A further object of the present invention is a spring that is moved by a pressure fluid pulse, such as an intake valve, an exhaust valve, and a fuel injection valve, or that exerts a force in a direction opposite to the force from the pressure fluid pulse. It is an object of the present invention to provide a method and an apparatus for making it possible to recycle the energy consumed when braking is applied to the movement of a part that is moved by a spring element.

A first object of the present invention is a method of the kind described at the beginning of the present specification, which prevents the outflow of liquid from a chamber filled with liquid when the piston / shaft reaches a predetermined position. It is achieved by a method characterized in that

A first object of the present invention is an apparatus of the type described at the beginning of the present description, comprising at least one valve for temporarily blocking the outflow of liquid from the chamber. This is achieved by the device characterized.

Claims 2 to 13, which are dependent claims, describe methods according to preferred embodiments of the present invention that are useful in achieving the first and other objects of the present invention.
The dependent claims, claims 15-30, describe an apparatus according to a preferred embodiment of the invention that is useful in achieving the first and other objects of the invention.

In particular, claim 9 describes a method according to a particularly preferred embodiment of the invention that enables the recycling of energy for braking.
Further, claim 20 describes a device according to a particularly preferred embodiment of the present invention corresponding to it.

  Other features and advantages of the method and apparatus according to the present invention will become apparent from the following detailed description.

Hereinafter, the present invention will be described with reference to specific embodiments with reference to the accompanying drawings.
FIG. 1 shows a pressure pulse generator according to the first embodiment. The illustrated device 1 includes a pressure fluid circuit 2, a cylinder 3, a piston 4 movably disposed in the cylinder 3, and a valve 5 mounted on a cylinder of the internal combustion engine. It is connected to. A detailed description of the internal combustion engine will be omitted. The internal combustion engine is, for example, a multi-cylinder engine including a plurality of cylinders, and each of the cylinders has a device 1 similar to the device 1 according to the present invention illustrated in order to operate a valve provided in the cylinder. It is preferable to provide one or more.

  The pressure fluid circuit 2 is connected to a pressure chamber 6 defined in the cylinder 3 through an inlet 7 that is a first opening and an outlet 9 that is a second opening. The inflow port 7 is connected to the pressure fluid supply unit 8, and the outflow port 8 is connected to the pressure fluid discharge unit 10. The pressure fluid is preferably a gas, and it is particularly preferable to use air or carbon dioxide among the gases. The pressure fluid supply unit 8 is preferably composed of a tank-equipped compressor mounted on the internal combustion engine, or may be composed only of a pressure tank. On the other hand, the pressure fluid discharge unit 9 may be any location as long as it is a location where the pressure is lower than the pressure generated by the pressure fluid supply portion 8, and may be, for example, a reflux path to the compressor. Valve bodies 43 and 44 are provided so that the pressure fluid circuit and the pressure chamber 6 can be communicated with each other by opening and closing the openings 7 and 9, and these valve bodies 43 and 44 are controlled by the pressure fluid. It is supposed to be. The valve bodies 43 and 44 are movably disposed in the valve chambers 45 and 46. The valve bodies 43 and 44 are controlled in accordance with fluctuations in pressure acting on one side of the valve bodies 43 and 44 in the valve chambers 45 and 46, and the one side referred to here is the opening 7 or 9. The side opposite to the side where it is formed. Further, each of the valve bodies 45 and 46 has a surface area in which the direction of pressure acting on the surface from the pressure fluid in the pressure fluid circuit 2 is the valve closing direction among the surfaces of the valve bodies. When the bodies 45 and 46 are seated on the peripheral portions of the openings 7 and 9 and close the openings 7 and 9, the pressure of the pressure fluid is larger than the area of the surface acting in the opposite direction.

  The pressure fluid circuit 2 includes two pressure fluid control valves, one of which is a first solenoid 11 and a first valve body 12 combined with the first solenoid 11. The other is composed of a second solenoid 13 and a second valve body 14 combined with the second solenoid 13. Furthermore, the illustrated device 1 is provided with a control device (not shown), which is connected to a sensor for detecting the position of the piston in the cylinder of the internal combustion engine, the sensor being a piston. The position of the piston may be directly detected, or the position of the piston may be indirectly detected by detecting the rotational angle position of the crankshaft, for example. The control device is connected to the solenoids 11 and 13 and controls the solenoids 11 and 13 to be energized based on information obtained from the sensors. Furthermore, a sensor 15 for detecting the position of the actuator piston 4 or the valve 5 is provided, and this sensor 15 is also connected to the control device via a wiring 16. Based on the information obtained from the sensor 15, the pressure fluid control valve is controlled to be de-energized.

  The solenoids 11 and 13 and the valve bodies 12 and 14 combined therewith are appropriately configured, and the pressure defined in the cylinder is controlled by controlling the solenoids to be in an energized state in a predetermined sequence. The pressure pulse can be sent into the chamber 6 through the first opening 7 with high accuracy, and the pressure pulse can be discharged from the pressure chamber 6 through the second opening 9 with high accuracy. .

The apparatus of the embodiment shown in FIGS. 1 to 3 includes a mechanism for hydraulic locking and braking. The hydraulic locking / braking mechanism includes a liquid- filled chamber 17 configured to allow liquid to flow in and out, and the actuator piston 4 is connected via a piston shaft 18 connected to the actuator piston 4. During the movement, the liquid is always in contact with the liquid in the chamber 17. When the actuator piston 4 is moved from the basic position to the remote position, the piston shaft 18 which is connected to the actuator piston 4 exits from the chamber 17, it flows the exit volume fraction of the liquid into the chamber 17. Further, when the actuator piston 4 moves in the opposite direction, the piston shaft 18 pushes out the liquid from the chamber 17 so that a braking effect is obtained. The mechanism shown in FIG. 1 includes a throttle unit 19. The throttle portion 19 in the illustrated example is ring-shaped, and when the actuator piston 4 and the valve 5 approach the basic position which is one end position, the piston shaft 18 is more specifically conical. The end portion 20 of the second end enters the ring-shaped throttle portion 19. When the actuator piston 4 and the valve 5 further approach the basic position, the gap between the end portion 20 of the piston shaft 18 and the throttle portion 19 is narrowed, thereby increasing the braking force. Therefore, this mechanism constitutes an oil damper type braking mechanism. Instead of providing the conical end portion 20 on the piston shaft 18, the shape of the throttle portion 19 may be such that its opening cross-sectional area gradually decreases in the moving direction when generating the braking effect. .

The mechanism further includes a liquid supply unit (not shown) and a connection channel 21 that connects the liquid supply unit and the chamber 17. Further, a check valve 22 is provided, and the check valve 22 opens to allow the liquid to flow into the chamber 17 from the liquid supply unit, allows the inflow, and tries to flow in the reverse direction. Closes the liquid . The liquid supply unit can be configured by an oil pump or the like equipped in the internal combustion engine.

The mechanism further comprises a downstream side of the connecting channel 23 for discharging the liquid from the chamber 17, the outflow destination of the liquid, if part of the lower pressure than the pressure which the liquid supply portion occurs, how For example, an oil pan of an internal combustion engine may be used. The operation valve 24 is a valve for setting the connection path between the chamber 17 and the low-pressure location via the discharge-side connection flow path 23 to a communication state and a cutoff state. In addition, an operation valve 24 is provided, which opens when the piston shaft 18 pushes liquid out of the chamber 17 as the piston 4 and the valve 5 move toward the basic position. It is like that. Further, actuation valve 24, when the piston 4 and the valve 5 is moved to this and opposite direction, Yes as closed, whereby the liquid in the connecting channel 23 for liquid discharge is the chamber 17 It is designed to prevent it from sucking in and backflowing. Since the liquid in the chamber 17 is heated as the piston 4 moves, the liquid and the ambient temperature may rise undesirably unless the reverse flow is prevented, and the operating valve 24 is Such inconvenience is provided to prevent temperature rise. The pressure of the liquid in the connecting passage 21 for liquid supply, when it is a state in which the liquid can flow into the chamber 17 from the connecting channel 21, to flow into without the liquid is interrupted, There is enough pressure.

FIG. 14 is a diagram showing another configuration example of the connection channel for discharging liquid . In the figure, connecting channel 23 for liquid discharge is connected to recirculating liquid to the connecting channel 21 for liquid supply connected to the upstream side of the check valve 22, i.e., the check valve 22 Connected to the liquid supply section. Similarly to the above-described embodiment, the mechanism shown in FIG. 14 also includes an operating valve 24 that opens and closes a connection channel for discharging liquid . According to this configuration, a certain amount of liquid circulates between the liquid supply unit and the chamber 17. Therefore, the liquid flowing through this mechanism is utilized with high utilization efficiency by the pump action. Further, in order to prevent a predetermined amount of liquid circulated and reused from being overheated and to lubricate the actuator piston 4 therewith, a flow path 52 is provided. Passage 52 has one end, out of the circulation flow path of the liquid, are connected to a portion of the connecting channel 21 for the liquid supply and the other end is connected to the cylinder housing the actuator piston 4 ing. Incidentally, the flow path 52, connecting portions of the one end, of the circulation path of the liquid, or as part of the connecting channel 23 for liquid discharge. What is important here is that a part of the liquid heated by performing the braking function flows out through the flow path 52. Although not shown in the drawing, this mechanism supplies the liquid after being supplied to the cylinder containing the actuator piston 4 and used for lubrication from a liquid supply unit such as an oil pan of an internal combustion engine. A reflux channel is provided for refluxing to a low pressure location. FIG. 14 also shows another example of the configuration relating to the method of controlling the operating valve 24 for discharging liquid , which will be described in more detail later.

One important feature of the present invention is that it allows the actuator piston 4 and more particularly the valve 5 to be locked in place. In particular, in the illustrated example, the valve 5 is prevented from returning to the basic position by being locked, and this is realized by temporarily preventing the liquid from flowing out of the chamber 17. . When the actuator piston 4 and the valve 5 reach a predetermined position, and preferably when the end position is reached, particularly when the end position, which is a remote position in the illustrated example, is reached, The valve 24 is kept closed so that the valve is locked. At this time, since the check valve 22 is closed, the liquid outflow from the chamber 17 is completely prevented. Has been. In order to release the lock, the operation valve 24 may be opened so that the liquid can be discharged through the liquid discharge connecting flow path. By utilizing these things, the valve timing can be made variable. On the other hand, the lift amount of the valve 5 from the valve seat is controlled mainly by selecting the length of time for sending the pressure fluid pulse from the first opening 7.

  Similarly to the two pressure fluid control valves 11 to 14 described above, the operation valve 24 can be constituted by a solenoid and a valve body. However, in the illustrated example, the operation valve 24 is operated by a pressure fluid. It is configured as a slave valve. In other words, the actuating valve 24 in the illustrated example is indirectly controlled by at least one pressure fluid control valve 11 to 14. In particular, in the illustrated example, the second solenoid 13 and the second valve body 14 are controlled. It is made to control by the pressure fluid control valve comprised by these.

The actuating valve 24 has a first surface in contact with the pressure fluid via the flow path 25 of the pressure fluid circuit 2, and the first surface of the actuating valve 24 includes the pressure fluid control valves 13, 14. The pressure fluid supply unit 8 and the pressure fluid discharge unit 10 are in communication with each other according to the operation position. The second surface of the actuating valve 24 opposite to the first surface is in contact with the liquid in the connection channel 23 for discharging liquid , thereby constituting a spring element in the form of a liquid spring. ing. Depending on whether the first surface of the working valve 24 is in communication with the pressure fluid supply unit 8 or the pressure fluid discharge unit 10, the working valve 24 has one of a valve closing position and a valve opening position. The actuating valve 24 that has moved to the open state is in communication with the connection channel 23 for discharging liquid . On the other hand, in another configuration example shown in FIG. 14, the surface on the opposite side is always in communication with the pressure fluid discharge portion 8 of the pressure fluid circuit 2 via the flow path 53. Therefore, not a liquid spring but a gas spring is configured. Also in the apparatus according to any embodiment shown in the drawings, the configuration change for changing the liquid spring Likewise the gas spring, or, it is possible configuration change for changing the gas spring to the liquid spring on the contrary .

2 and 3 are diagrams showing an example of a modified configuration of the chamber 17 described above. In this modified configuration example, the shape of the end portion 20 of the piston shaft 18 is made different, and even when the end portion 20 having this shape is employed, an appropriate braking effect can be obtained. In this modified configuration example, the size and shape of the chamber 17, by the one corresponding to the size and shape of the portion that enters into the chamber 17 of the piston shaft 18, defines a throttle portion . However, the end of the end portion 20 of the piston shaft 18 is formed in a frustoconical shape. In the final part of the braking operation, i.e. just before the actuator piston 4 and the valve 5 reach the basic position, the gap between the throttle and the piston shaft 18 is constant because the end 20 of the piston shaft 18 The portion 48 having a certain length following the frustoconical portion 47 has a constant cross-sectional area, or at least its outer peripheral surface is parallel to the inner peripheral surface 49 of the throttle portion. Because.

  4 to 13 are diagrams showing another configuration example of a hydraulic braking and locking mechanism provided in the pressure pulse generator, and the braking / locking mechanism of this another configuration example has a considerable amount thereof. The portion is configured similarly to the brake / lock mechanism described above.

FIGS 13 braking / locking mechanism shown in the second chamber 26 is a chamber of the cylinder-shaped, a second piston 27 which is movably disposed in the second chamber 26, the second chamber 26 And a spring element 28 that acts on the second piston 27. First chamber 17 described above are connecting to the cylinder-shaped second chamber 26, whereby, from the first chamber 17, the cylinder-shaped second chamber 26, to one side of the piston 27, so that liquid can flow It has become. The spring element 28 functions to absorb energy by causing the second piston 27 to act on the second piston 27 in a direction opposite to the moving direction when the second piston 27 moves in one moving direction. It is. The spring element 28 in the illustrated example is a spring member as a mechanical component disposed in the cylinder-shaped second chamber 26, and is attached to the opposite side of the piston 27 to the side connected to the first chamber 17. Power is acting. When the actuator piston 4 and the valve 5 move toward the basic position, liquid is pushed out from the first chamber 17 accordingly, and the spring element 28 absorbs energy at that time.

Similar to the configuration example described above, the mechanism according to this configuration example also has a connection channel 21 for supplying liquid between the first chamber 17 and the liquid supply unit, and between the first chamber 17 and the low pressure portion. And a connection flow path 23 for discharging liquid . Further comprising a check valve 22, the check valve 22, the liquid, and tends to flow from the liquid supply unit is a high-pressure position, the first chamber 17 via the connecting channel 21 for the liquid supply When the valve is opened, the valve is closed when it is going to flow in the opposite direction. Further, an operation valve 29 is provided. The operation valve 29 includes a solenoid 30 and a valve body 31 that is driven by the solenoid 30 to bring the connection flow path 23 for discharging liquid into a communication state and a cutoff state. ing. One side of the valve body 31 of the actuating valve 29 is in contact with the pressure fluid via the connection flow path 50, thereby constituting a spring element 50 in the form of a gas spring. The spring element 50 applies a force in the opposite direction to the force acting on the valve body 31 from the energized solenoid 30 to the valve body 31, and when the solenoid 30 is in the deenergized state, the valve body 31 is returned to the original position, and the connection flow path 23 for discharging the liquid is shut off.

The mechanism further includes an operating valve 32 that brings the connection path between the first chamber 17 and the cylinder-shaped second chamber 26 into a communication state and a cutoff state. The “cylinder-type second chamber ” referred to herein includes a flow path that defines a connection path between the cylinder-type second chamber 26 and the first chamber 17. In the illustrated configuration example, the piston 27 includes a piston shaft that forms a part of the piston 27. As illustrated, the piston shaft is connected to the cylinder-shaped second chamber 26 and the first chamber . It is fitted into a flow path that defines a connection path to the chamber 17.

The check valve 33 incorporates two check valves 33, 34. The check valve 33 allows only liquid to flow from the first chamber 17 to the cylinder-shaped second chamber 26, The other check valve 34 is configured to allow only liquid to flow from the cylinder-shaped second chamber 26 into the first chamber 17.

The connection flow path connecting the first chamber 17 and the cylinder-shaped second chamber 26 includes two flow paths 35 and 36 parallel to each other. The operating valve 32 includes a valve body 38 that can move through the two flow paths 35 and 36, and at least one through hole 37 that is a flow opening is formed in the valve body 38. ing. One check valve 33 of the two check valves 33, 34 is constituted by a biased valve body disposed in one flow path 35, and the other check valve 34 is The energized valve body is disposed in the other flow path 36. The two urged valve bodies are disposed on opposite sides of the valve body 38.

  The valve body 38 of the operating valve 32 is movable between the first position and the second position. When the valve body 38 is moved to the first position, the through hole 37 that is a flow opening is located in the one flow path 35. When moved to the second position, the through hole 37 which is a flow opening is positioned in the other flow path 36. Due to the movement of the valve body 38, one of the two check valves 33 and 34 becomes functional. It should be noted that the term “located within the flow path” is used herein in a broad sense, and the flow opening does not necessarily need to be completely coincident with the flow path, but is completely coincident. It can be said that it is preferable.

The actuating valve 32 is controlled by the pressure fluid via at least one connection flow path 39 connected to the pressure fluid supply unit 8 or the pressure fluid discharge unit 10. The method of controlling the operation valve 32 is the same as the method of controlling the operation valve 24 provided in the connection channel 23 for discharging liquid , which has been described with reference to the first and second configuration examples. That is, the operating valve 32 is configured such that the first surface 40 is in contact with the pressure fluid via the flow path 25 of the pressure fluid circuit 2, and the first valve 40 is in accordance with the position of the control valves 13 and 14. The surface 40 is in communication with either the pressure fluid supply unit 8 or the pressure fluid discharge unit 10. The second surface 41 of the actuating valve 32 opposite to the first surface is in contact with a liquid having a given pressure. In particular, in the illustrated example, the liquid is supplied via the connection channel 21 for supplying liquid. It is in contact with the liquid in the supply section. Depending on whether the first surface 40 of the working valve 32 is in communication with the pressure fluid supply unit 8 or the pressure fluid discharge unit 10, the working valve 32 brings the check valve 33 into a functional state. It moves to one of the position and the position where the check valve 34 is put into a functional state. The flow path on which the check valve is not functioning is closed by the valve body 38. In the present invention, when the actuator piston 4 and the valve 5 are moved to the basic position, the check valve 33 that allows the liquid to flow from the first chamber 17 to the cylinder-shaped second chamber 26 is made into a functional state. When the actuator piston 4 and the valve 5 are moved in the opposite direction, that is, to a remote position, the check valve 34 that allows the liquid to flow from the cylinder-shaped second chamber 26 to the first chamber 17 is put into a functional state. I have to.

  According to the configuration shown in FIGS. 4 to 13, most of the energy used for braking when the actuator piston 4 and the valve 5 approach the basic position is absorbed by the spring element 28, and The absorbed energy is not simply converted to heat and lost as in the pure oil damper type braking mechanism shown in FIGS. 1 to 3, but recycled when the valve moves in the reverse direction. It becomes like this.

Further, in this configuration, the operation valve 29 provided in the connection channel 23 for discharging the liquid is related to when the movement of the actuator piston 4 and the valve 5 to the basic position stops, immediately after the stop, or at the stop time. At some point, the valve is temporarily opened only for the purpose of discharging the remaining liquid , so that the actuator piston 4 and the valve 5 can be fully returned to their basic positions. If the connection flow path 23 for discharging the liquid is not provided, the valve 5 cannot be completely returned to the basic position only by the resilient force of the valve spring 42 due to energy loss in the mechanism. The operating valve 29 is closed when the actuator piston 4 and the valve 5 reach the basic position, and the control for closing the valve is performed based on the information obtained from the sensor 15 mentioned above.

One particularly important configuration example of the present invention is as follows. The configuration example is such that the pressure chamber defined in the cylinder 3 into which the liquid contains pressure fluid for moving the actuator piston and into which the pressure fluid flows in and out is a chamber . In this case, the oil damper type braking mechanism itself functions as a pressure pulse generator. Further, in this case, the actuator piston is moved by supplying the liquid pulse supplied through the connection flow path for liquid supply such as the connection flow path 21 connected to the liquid supply unit to the chamber 17. Become. Furthermore, an actuating valve, which is a valve mechanism for controlling the duration of the liquid pulse, is also configured as a part of the mechanism. Therefore, the pressure fluid circuit as described above is not necessary. Further, if the operation valve 32 is controlled by a solenoid, the pressure fluid as described above is completely unnecessary. In any of the embodiments described above, the spring element to be equipped can be any of a gas spring, a liquid spring, and a mechanical spring member.

4 to 13 are views showing each state in a series of stages of the opening / closing cycle of the actuator piston 4 and the valve 5.
In the state of FIG. 4, the engine valve 4 is in the basic position. Compressively by a spring element 28, via the piston shaft and by applying a pressing force to the piston 27, the pressing force is working in the direction of flowing the liquid into the first chamber 17. Operated valve 32 is in a position to prevent the liquid from flowing into the first chamber.

In the state of FIG. 5, the operating valve 32 has moved to the other position, so that the piston 27 can move, and the liquid can flow to the first chamber 17.

In the state shown in FIG. 6, the piston 27 is moving, the liquid is flowing, and the piston shaft 18 connected to the actuator piston 4 starts to move.
FIG. 7 shows a state where the piston 27 has moved to the end position.

In the state shown in FIG. 8, since the pressure fluid pulse continues, the shaft of the actuator piston 4 is slightly moved further, and accordingly, the first via the connection channel 21 for liquid supply. Liquid is flowing into the chamber 17.

In the state of FIG. 9, the actuator piston 4 and the valve 5 have reached the end position, and the operation valve 32, the check valve 22, and the operation valve 29 are all closed, and the liquid from the first chamber 17 Outflow is prevented, so that the actuator piston 4 and the valve 5 are locked at the end positions, which are remote positions.

FIG. 10 shows that since the operating valve 32 has returned to its original position, liquid can flow from the first chamber 17 to the second piston 27, whereby the actuator piston 4 and the valve 5 of the internal combustion engine can move. It shows the stage when it became a state.

In the state shown in FIG. 11, the actuator piston 4 further moves toward the basic position, more liquid flows from the first chamber 17 into the second chamber 26, and the second piston 27 further moves. ing.

FIG. 12 shows the state when the movement has been completed, but the engine valve has not yet fully reached its basic position due to energy loss.
FIG. 13 shows that when the state shown in FIG. 12 is reached or just before that state, the liquid discharge operation valve 29 is opened so that the liquid can flow out from the first chamber 17. Therefore, it has been moved to the basic position of the engine valve pixel. When the engine valve reaches the basic position, the operating valve 29 is closed again, thereby returning to the state shown in FIG.

  Of course, those skilled in the art can easily correspond to other embodiments included in the scope of the present invention. The scope of rights to be protected is as specified by the description of the claims, and the description of the claims is based on the description of the detailed description of the invention and the description of the drawings.

Any check valve used, as is generally the case, is a spring that urges the check valve to press against the valve seat of the opening that the check valve opens and closes. It is preferable to provide a mechanism. In FIG. 2, a spring mechanism provided in the check valve 22 interposed in the connection flow path 21 for supplying liquid is illustrated by a spring 51.

1 is a schematic cross-sectional view of a pressure pulse generator provided with a hydraulic lock / brake mechanism according to one embodiment of the present invention. FIG. 5 is a schematic cross-sectional view of a pressure pulse generator provided with a hydraulic lock / brake mechanism according to another embodiment of the present invention. FIG. 3 is a schematic view showing only a part of the lock / braking mechanism of FIG. 2 taken out. It is a schematic diagram of a hydraulic lock / braking mechanism according to another embodiment of the present invention, and is a diagram showing one state of a series of states of the mechanism. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is the schematic diagram which showed one state in the series of states of the mechanism of FIG. It is a schematic diagram of the mechanism which concerns on another embodiment of this invention.

Claims (28)

Move the piston (4) in the first direction in the cylinder (3) by temporarily allowing the flow of pressure fluid into the cylinder (3) to one side of the piston (4) Thereafter, the piston (4) is moved in the second direction while temporarily allowing the inflowing pressure fluid to flow out from the cylinder (3), and is connected to the piston (4). The shaft (18) that moves together with the piston (4) can flow in hydraulic fluid from the cylinder (3) via the check valve (22), and between the valve open position and the valve close position. of the liquid-pressure liquid via a controllable valve (24, 29) can flow out, extends to filled with liquid chamber (17), said shaft (18) is the first way the piston to direction ( When 4) moves, the check valve (22) And allowing the inflow of liquid into the chamber (17), when the second way the piston direction (4) moves, the liquid via said controllable valve (24, 29) said chamber In the piston control method of extruding from (17),
When the piston (4) and the shaft (18) reach a predetermined position, the piston (4) and the shaft (18) close the controllable valves (24, 29) to close the first valve. 2-way transfer to the direction is temporarily blocked to prevent the outflow of liquid from said chamber (17), piston control method, characterized in that.   The liquid flow out of the chamber (17) filled with liquid before or when temporarily allowing the flow of the pressure fluid into the cylinder (3). The method of claim 1, wherein the method is to prevent it.   3. A method according to claim 1 or 2, wherein the chamber is closed when the piston (4) or the shaft (18) reaches a first end position.   4. The liquid is allowed to flow out of the chamber when the piston (4) or the shaft (18) reaches the second end position. 5. the method of.   The piston (4) is connected to an intake valve or an exhaust valve (5) of the internal combustion engine, is connected to a fuel injection valve that injects fuel into the combustion chamber of the internal combustion engine, or has a compression ratio. In order to make it variable, it is connected to a piston arranged in a cylinder provided in the combustion chamber of the internal combustion engine, or constitutes a compression ratio variable piston itself, and the compression ratio variable The method according to any one of claims 1 to 4, wherein the movement amount of the piston or the valve (5) is directly proportional to the movement amount of the piston (4) or the shaft (18).   The pressure fluid is a pressure gas, and by temporarily allowing the pressure gas to flow into the cylinder (3), the piston (4) is moved in a first direction, and the piston (4) 6. The method as claimed in claim 1, wherein the pressure gas is discharged from the cylinder (3) by moving in a reverse direction.   The chamber (17) is disposed outside the cylinder (3), and the shaft can enter the throttle portion (19) disposed in the chamber (17) and existing in the liquid. 7. A method as claimed in any one of claims 1 to 6, which is configured as described above.   A gap between the shaft (18) and the inner periphery of the throttle part (19) surrounding the shaft (18) enters the throttle part (19) into the shaft (18). 8. The method of claim 7, wherein the method narrows as the time elapses. The chamber (17) is connected to a cylinder-shaped second chamber (26), and a second piston (27) is movably disposed in the cylinder-shaped second chamber (26). A spring element (28) for applying an urging force to the second piston (27) is disposed, and to one side of the second piston (27) in the cylinder-shaped second chamber (26), Yes as it can be and out flow of the liquid, said piston (4) or when the sheet Yafuto of the piston (4) (18) moves so as to enter into the liquid in the chamber (17) in The liquid flows into one side of the second piston (27) in the cylinder-shaped second chamber (26) against the biasing force of the spring element (28). The method of any one of thru | or 6.   When the movement of the piston (4) or the shaft (18) is stopped by the biasing force of the spring element (28) against the movement, the cylinder-shaped second chamber (26) to the chamber (17) The method according to claim 9, wherein the liquid is prevented from flowing back into the apparatus.   When the movement of the piston (4) or the shaft (18) is substantially stopped by the biasing force of the spring element (28) resisting the movement, a connection flow path for discharging liquid from the chamber (17) 11. A method according to claim 9 or 10, wherein liquid is allowed to flow out temporarily via (23).   When the liquid is prevented from flowing out of the chamber (17), the liquid can flow from the cylindrical second chamber (26) to the chamber (17) filled with the liquid. 12. The method according to claim 10 or 11, wherein: A cylinder (3);
A piston (4) movably disposed in the cylinder (3);
An inlet (7) to the cylinder (3) and an outlet (9) from the cylinder (3), the inlet (7) and the outlet (9) being one of the pistons (4) A pressure fluid circuit provided on the side;
A shaft (18) connected to the piston (4) and moving with the piston (4);
A chamber (17) through which the shaft (18) enters and exits as the piston (4) moves in the cylinder (3);
A control device for a piston comprising: at least one valve (22, 24, 29, 32) for temporarily blocking outflow of liquid from the chamber (17);
The piston (4) is moved in the first direction in the cylinder (3) by temporarily allowing inflow of pressure fluid into the cylinder (3) to one side of the piston (4). And then moving the piston (4) in the second direction while temporarily allowing the inflowing pressure fluid to flow out of the cylinder (3),
The shaft (18) is a valve (24, 29) through which hydraulic liquid can flow from the cylinder (3) via a check valve (22) and can be controlled between a valve opening position and a valve closing position. ) which can flow out said fluid-pressure liquid via a extends to the chamber (17) filled with liquid, when the first way the piston to direction (4) is moved, said check valve (22 ) through to allow the flow of liquid into the chamber (17), when the second way the piston direction (4) moves, the liquid via said controllable valve (24, 29) Extruded from the chamber (17),
When the piston (4) and the shaft (18) reach a predetermined position, the piston (4) and the shaft (18) close the controllable valves (24, 29) to close the first valve. It moved temporarily blocked in 2-way to the direction, to prevent the outflow of liquid from said chamber (17), the control device of the piston, characterized in that. The piston (4) is connected to an intake valve or an exhaust valve (5) of the internal combustion engine, is connected to a fuel injection valve that injects fuel into the combustion chamber of the internal combustion engine, or has a compression ratio. 14. The piston according to claim 13 , which is connected to a piston arranged in a cylinder provided in a combustion chamber of an internal combustion engine for making it variable, or constitutes such a compression ratio changing piston itself. Piston control device. The chamber (17) filled with liquid is disposed outside the cylinder (3), and the shaft (18) extends into the chamber (17) in a sealed state with respect to the liquid. The control device for a piston according to claim 13 or 14 . The piston control device according to any one of claims 13 to 15 , wherein the pressure fluid in the pressure fluid circuit (2) is a gas. Comprising a throttle portion disposed in said chamber (19), said shaft (18), any one of claims 13 to 16 is disposed so as to move the narrowed portion (19) in Piston control device. The shape of the shaft (18) or the throttle part (19) is gradually narrowed in the direction in which the shaft (18) enters, whereby the shaft (18) passes through the throttle part (19). as) moves the direction of one piston control according to any one gap of claims 13 to 17 are to be reduced between the narrowed portion (19) and said shaft (18) apparatus. A cylinder-type second chamber (26), a piston (27) movably disposed in the cylinder-type second chamber (26), and the cylinder-type second chamber that applies a biasing force to the piston (27). A spring element (28) disposed in the chamber (26), the chamber (17) being connected to the cylinder-shaped second chamber (26), whereby the cylinder-shaped second chamber ( 26), in order to the liquid to one side of the piston (27) flows, when said piston (27) is moved into the direction of one, said spring element (28), the piston ( The piston control device according to any one of claims 13 to 16 , wherein energy can be absorbed by applying a biasing force in a direction opposite to the moving direction of (27). The piston control device according to claim 19, further comprising a valve (32) for bringing a connection path between the chamber (17) and the cylinder-shaped second chamber (26) into a communication state and a shut-off state. The valve includes a check valve (33), and the check valve (33) is configured to allow liquid to flow only in the direction from the chamber (17) to the cylinder-shaped second chamber (26). The control device for a piston according to claim 20 . The valve is provided with another check valve (34) which flows liquid only in the direction from the cylinder-shaped second chamber (26) to the chamber (17). The piston control device according to claim 20, which is configured as described above. The connection flow path connecting the chamber (17) and the cylinder-shaped second chamber (26) includes two flow paths (35, 36) parallel to each other, and the valve (32 ) Includes a valve body (38) movable through the two flow paths, and at least one through hole (37) as a flow opening is formed in the valve body (38). The piston control device according to any one of claims 19 to 22 . The valve body (38) of the valve (32) is movable between a first position and a second position. When the valve body (38) is moved to the first position, the through hole (37) which is a flow opening is formed. The through-hole (37), which is a flow opening, is located in one of the two flow paths (35, 36) and moves to the second position. 24. The piston control device according to claim 23 , wherein the control device is located in the other flow path of the passages (35, 36). It said valve (32), or are to be directly controlled by a solenoid (12), or, according to claim 20 to 24 are to be indirectly controlled by a solenoid (12) via a pressure fluid circuit The piston control device according to any one of the above. The piston control according to any one of claims 13 to 25 , wherein the chamber (17) is connected to a pressure supply source of the liquid via a connection flow path ( 21 ) which is an inflow path into the chamber. apparatus. 27. The piston control device according to claim 26, further comprising a valve (22) for blocking a flow in a direction from the chamber (17) to the pressure supply source. Said chamber (17) a small amount from the discharge passage in which the connection channel (23) said chamber through from (17) liquid-operated valve which opens and closes for discharging the claims 13 to 26 comprising (29) The piston control device according to claim 1.

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